FORCE APPLYING DEVICES

Abstract: A force applying device such as a spring supporting device comprises a helical compression spring (1) located within a cylindrical housing (3), the device being designed to support a load (8) through a rod (5). In use, the load (8) will move vertically between a high position and a low position, involving compression and extension of the spring (1). One end of the spring is provided with a pair of diametrically projecting trunnions (9), which are located within a pair of diametrically opposed cam tracks (11) provided in the cylinder wall. During initial downward movement of the load, the trunnions engage with the cam track (11), tending to "wind up" the spring, providing an upward force acting on the trunnions. During final movement, movement of the trunnions within the cam track allows the spring to "unwind", and thus some of the work required to be performed during this axial movement of the load produces a downward force compensating the increase in spring reaction. In this manner, by selection of a cam track of appropriate shape, a substantially constant force may be produced acting against the load throughout the range of movement of the spring.

Description: Title: Force Applying Devices Description of Invention This invention is concerned with improvements relating to force applying devices, and will be described herein as used in a supporting device of the kind used to provide support for an article over a range of movement thereof, and has been devised particularly but not exclusively for use in the provision of a support for pipework. For example, in many industrial chemical processes, it is necessary to support pipework by the use of a constant force, allowing the pipework to be supported correctly, despite variations in the position of the pipework caused by (for example) thermal expansion. A convenient method of providing a support for pipework is to utilise a spring, using the reactive force either of a compression spring or of a tension spring. However the reactive force provided by a spring is not constant over its operative range, and varies in direct proportion with the spring rate relative to the axial compression or extension of the spring. Specifically, where a load is being supported by a compression spring, the reactive force increases as the spring is compressed, and decreases as the spring is relaxed in direct proportion to the spring rate. Similarly, where a load is being supported by a tension spring, the reactive force increases as the spring is extended, and decreases as the spring is relaxed. Thus, whilst the variations in the reactive force may be used advantageously in certain circumstances, when attempting to support pipework by constant load, the use of springs causes difficulty. Many suggestions have been made to provide a supporting device which generates a substantially const." ^t reactive force over its operating range. Generally these devices utilise comb. a. uons of bell cranks and levers operating through slide and rotation bearings to change the overall characteristics of the support. However bell crank and lever geometry provides an eccentric shape that has to be bolted to a supporting structure, or alternatively the eccentric geometry will give rise to considerable turning moments. Additionally whilst theoretically it is possible to provide a substantially constant load support, in practice it is difficult and expensive to maintain the device in satisfactory working condition. According to this invention there is provided a method of changing the reactive force of a spring device (e.g. supporting or other force-applying device) in which linear movement of the load is utilised to produce a torsional force on the spring, the effect of the torsional force being to reduce or negate the changes in the reactive force produced by said spring as a result of said linear movement. Where movement of the spring under load would result in a reduction in the spring reaction, such movement may be utilised to "wind up" the spring to require the work done by the load per unit movement to increase, and by balancing the rate of "wind up" with the reduction in the spring reaction, a substantially constant force resisting such movement may be obtained. Similarly where movement of the spring under load would result in an increase in the spring reaction, such as occurs during compression of the spring, such movement may be utilised to cause or allow the spring to unwind reducing the work done per unit movement of the spring to achieve a substantially constant force. Preferably however during the range of movement of the load such movement is utilised to cause wind up of the spring from an initial position towards a median position, and subsequently to allow the spring to relax (unwind) from said median position. Such a construction is particularly suitable for use where the spring is supporting the load under compression. Alternative to the use of the spring itself to provide the torsional force, other means may be utilised, such as a separate spring, such as an axial torsion spring, or torsion bar. According to this invention there is also provided a method of changing the reactive force produced by the spring of a spring supporting or force device by arranging a torsional force to react on cams or guides to cause an axial force, compensating with load movement, to reduce or negate changes in the spring reactive forces that would otherwise occur due to supporting spring compression or tension. Conveniently the torsional force is achieved by pre-winding of the load-carrying compression or tension spring, but could be achieved by other means, e.g. a torsion bar or separate torsion spring. Where movement of the compression or tension spring under load would result in a reduction in the spring reaction the cams or guides may be so arranged that a force acting axially with the spring is developed by the torsional force thus adding to the spring force to provide a combined axial force as derived according to the particular point of load travel. Similarly where movement of the spring under load would result in an increase in the spring reactive force such as occurs during compression or tensioning of the spring, the cams or guides may be so arranged that a force acting axially against the spring is developed by the torsional force thus subtracting from the spring force to p- ide a combined axial force as desired according to the particular point of lo. travel. Preferably but not essentially the spring is arranged to balance the load at the mid point in the load design travel and the cam o guide means are so arranged that no axial force is developed by the torsional „orce at this point. According to this invention there is also provided a force applying device comprising a housing adapted to be secured to a supporting surface, a spring supported by the housing, and means to enable a load to be secured to the spring to be supported thereby, characterised by the provision of a compensating means to provide an additional axial force acting on the load varying in dependence upon load movement to compensate for variations in the reactive force provided by the spring during movement of the load. Said compensating means may be operative to cause the device to produce a substantially constant reactive force on axial movement of the load, alternatively the compensating means may be operative to cause the spring to produce a predetermined variable reactive force on axial movement of the load. The compensating means may be operative to produce a torsional force on the spring throughout the range of movement thereof; or may be operative to produce a torsional force on the spring throughout part only the range of movement thereof. Preferably however the compensating means is operative to apply a torsional force to the spring in one direction (e.g. increasing) during movement of the load at one end of its range of movement, and is operative to apply a torsional force to the spring or to have applied thereto in the opposite direction (e.g. decreasing) during movement of the load at the other end of its range and movement. For example the compensating means may be operative to apply a horizontally developed force to the spring which varies from a maximum in one direction to zero, and then varies from zero to a maximum in the other direction. Preferably the device comprises a cylindrical housing, trunnion means being provided which is secured to the spring (either directly or indirectly) projecting diametrally therefrom, said trunnion means engaging with diametrally opposed cam or guide tracks (hereinafter referred to as "cam tracks" for convenience) provided in the wall of the cylindrical housing, and so arranged that the trunnion means rotates about the longitudinal axis as the load supported by the spring moves longitudinally. Preferably the cam faces are so inclined in the longitudinal direction as to reduce the effect of the variation in the axial force applied to the load due to the spring rate of the spring during axial movement of the load supported thereby. There will now be given a detailed description, to be read with reference to the accompanying drawings, of a force applying device which is a preferred embodiment of this invention, having been selected for the purposes of illustrating the invention by way of example. In the accompanying drawings: Figure 1 shows the variation in reactive force of a conventional spring supporting device during axial movement of a load supported thereby; Figure 2 is a sectioned front elevation of the pipe support device which is a preferred embodiment of this invention, the device being shown supporting a pipe load at a high position; Figure 3 is an external side elevation of the device, showing the pipe load at a low position; and Figure 4 shows the variation in the reactive force in a spring supporting device which may be obtained by the use of this invention. The supporting device which is the preferred embodiment of this invention comprises a helical compression spring 1 located within a cylindrical housing 3, the device being designed to support a load 8, typically but not exclusively a pipe, from a fixed support structure 7. A rod 5 is secured to an upper spring cap 2 mounted on an upper end portion of the spring 1, the lower end of the spring being secured to a base cap 4. A top plate 15 of the housing is provided with a lug 16 for attachment, through a stirrup hanger 6, to the support structure 7. The base cap 4 is provided with a pair of diametral trunnions 9 which are located in axially extending slots 12 in the housing 3. The base cap is threaded on to a threaded sleeve adjuster having a double flanged lower end 17 which embraces the base plate 14, enabling the sleeve 13 to be rotated through a central aperture in the base plate 14 whilst locating the sleeve axially, the load rod 5 passing freely through the base cap 4 and base plate 14. In this manner the position of the base cap may be adjusted axially by rotation of the adjuster 13 to vary the reactive force provided by the spring, and hence enabling the load bearing capacity of the device to be adjusted. In use, the pipe load 8 will move vertically during plant operation to any position between the high position shown in Figure 2 and the low position shown in Figure 3. The pipe load 8 is hung from the load rod 5 and as the load moves downwardly the load rod pulls the upper cap 2 downwardly, to compress the spring. The device which is the preferred embodiment of this invention comprises means to compensate for variations in the force applied by the spring to the load as the load moves axially, and specifically is operative to negate the variation of the spring reaction of the spring as the spring is compressed and relaxed. In the preferred embodiment the compensation means comprises a pair of trunnions 10 extending diametrally from the cap 2 which coact with cam surfaces formed as a curved cam track 11 in the wall of the cylindrical housing the trunnions sliding or rolling along the cam track. In the preferred embodiment the helical compression spring 1 is arranged to balance the pipe load 8 at the mid point M of its range of axial movement so that when the pipe load is at the high position as shown in Figure 2, the resilience of the spring in compression would be insufficient to support the pipe load, as is evident from Figure 1. In particular, the variation in the spring rate of a conventional spring is shown in Figure 1 and it will be seen that, as the spring is compressed, the spring reaction increases. If the spring correctly balances the load at the median point M, at the commencement of downward travel of the load at the position Ml, the load is under-supported by X, whilst at the end of its range of travel, at the position M2, the force provided by the spring to counterbalance the load is too great by Y. In the preferred embodiment the additional support provided on movement of the load from the positions Ml to M is provided by requiring the load as it moves downwardly to perform additional work as the spring is compressed towards the position M, said additional work being in the form of "winding up" the spring as the load moves downwardly. During such initial movement the trunnions engage with the face 11a of the cam track 11, providing an upward force acting on the trunnions. The rate at which this work is required to be performed is dependent upon the angle of the cam face 11a, and as the spring is compressed towards its median point, the work required to be performed to produce a constant balancing force reduces, and at the median point, the cam face 11a is parallel to the longitudinal axis. Thus by precompressing the spring so that it balances at the median point M (such precompressing being obtained by rotation of the adjuster 13), and providing an appropriately shaped cam track 11, the additional force X may be applied in the upward direction to the trunnions by the reactive force acting vertically on the trunnions (the horizontal components cancelling out), the force reducing as the load moves towards its median points. As the spring is compressed towards its median position, the work required to be performed to produce a constant spring reaction reduces, and at the median point, the cam track is parallel to the longitudinal axis. As the spring is compressed beyond the median point, some of the work required to be performed during further compression of the spring is obtained by allowing the spring to "unwind" - that is, a downward force is applied to the trunnions by engagement thereof with the lower face lib of the cam track 11, said downward force increasing from zero at the median point to the maximum Y at the low position M2 of the load. In this manner, by appropriately shaping of the cam track 11, the counterbalancing force applied to the load by the support device may be adjusted to a constant level Z - that is, the level obtained by the spring at its median point - throughout the range of travel of the load. In practice, as can be seen from Figure 4, a small hysteresis is found to be produced. However it is believed that this hysteresis may be reduced by providing smooth running between the trunnions and the cam track. Nonetheless, a significant improvement in the constancy of the supporting force may be obtained by the ^ se of the invention. Whilst in the preferred embodiment a cam track is utilised which has a shape which will produce a substantially constant supporting force acting against the load throughout the range of movement of the spring, since the cam surface profile will determine the supporting effort applied to the load rod 5, within limits, any support pattern may be obtained. Thus if desired a bias may be provided to ensure that the load will tend to move to a preferred position. Whilst in the preferred embodiment the spring is a compression spring, if desired the same effect may be achieved when a tension spring is utilised. As will be appreciated, whilst in the preferred embodiment a compensating axial force is obtained by the torsion force operating between the trunnions and the spring, if desired the compensating force may be applied to the main spring by other means, and in particular a torsion bar or separate, compensating spring may be utilised to provide a compensating force which is dependent upon load movement, and which may be utilised to reduce or negate the variations in the supporting force which would otherwise be produced. Additionally whilst in the preferred embodiment the compensating force is obtained by engagement of the trunnions with the cam face of a cam track, other guide means may be utilised, and such is to be deemed to be included within the term "cam means". Further, whilst the invention has been described in relation to a device for supporting an article, it will readily be understood that the principles of the invention may be utilised to provide a constant force in other circumstances wherein the force would vary according to load movement. Thus the invention may be utilised in any force applying device of this general kind, and is to be deemed to be included within the term "supporting device" as used herein. The features disclosed in the foregoing description, or the following claims, or the accompanying drawings, expressed in their specific forms or in terms of a means for performing the disclosed function, or a method or process for attaining the disclosed result, as appropriate, may, separately or in any combination of such features, be utilised for realising the invention in diverse forms thereof.

Claims: CLAIMS 1. A method of changing the reactive force of a spring supporting device in which linear movement of the load is utilised to produce a torsional force on the spring, the effect of the torsional force being to reduce or negate the changes in the reactive force produced by said spring as a result of said linear movement. 2. A method according to Claim 1 wherein to produce or negate a reduction in the spring reaction, such movement is utilised to "wind up" the spring to require the work done by the load per unit movement to increase. 3. A method according to one of Claims 1 and 2 wherein to reduce or negate a decrease in the spring reaction, such movement is utilised to cause or allow the spring to unwind reducing the work done per unit movement of the spring to achieve a substantially constant force. 4. A method of changing the reactive force produced by the spring of a spring supporting or other force device by arranging a torsional force to react with cams or guides to cause an axial force, compensating with load movement, to reduce or negate changes in the spring reactive force that would otherwise occur due to compression or tension of the supporting spring. 5. A force applying device comprising a housing adapted to be secured to a supporting surface, a spring supported by the housing, and means to enable a load to be secured to the spring to be supported thereby, characterised by the provision of a compensating means to provide an additional axial force acting on the load which varies in dependence upon load movement to compensate for variations in the reactive force provided by the spring during movement of the load. 6. A device according to Claim 5 wherein the compensating means is operative to cause the device to produce a substantially constant reactive force on axial movement of the load. 7. A device according to one of Claims 5 and 6 wherein the compensating means is operative to produce a torsional force on the spring throughout the range of movement thereof. 8. A device according to one of Claims 5 and 6 wherein said variation means is operative to produce a torsional force on the spring throughout part only of the range of movement thereof. 9. A device according to any one of Claims 5 to 8 wherein the compensation means is operative to apply a torsional force to the spring in one direction during movement of the load at one end of its range of movement, and is operative to apply a torsional force to the spring or to have applied thereto in the opposite direction during movement of the load at the other end of its range of movement. 10. A device according to any one of Claims 5 to 9 comprising a cylindrical housing, trunnion means being provided which is secured to the spring projecting diametrally therefrom , said trunnion means engaging with diametrically opposed cam or guide tracks provided in the wall of the cylindrical housing, and so arranged that the trunnion means rotates about the longitudinal axis as the load supported by the spring moves longitudinally. 11. A device according to Claim 10 wherein the cam faces are so inclined to the longitudinal direction as to reduce the effect of the variation in the axial force applied to the load due to the spring rate of the spring during axial movement of the load supported thereby. 12. A method of changing the reactive force produced by the spring of a spring supporting device, when carried out substantially as hereinbefore described with reference to the accompanying drawings. 13. A spring supporting device constructed and arranged substantially as hereinbefore described with reference to the accompanying drawings.

Inventors: POPPLEWELL PETER LESLIE, POPPLEWELL, PETER, LESLIE
Applicants: POPPLEWELL PETER LESLIE, POPPLEWELL, PETER, LESLIE
Application year: 1994
Main classification: F16L3
IPC codes: B60G11, F16F1, F16L3